Power transmission and speed reducer



May 16, 1939. J. F. JAWOROWSKI POWER TRANSMISSION AND SPEED REDUGERFiled Aug. 28, 1957 9 Sheets-Sheet l .gm t

J- P- 'J'HWURUWSKI 9 Sheets-Sheet 2 May 16, 1939. J. F. JAWOROWSKI POWERTRANSMISSION AND SPEED REDUCER Filed Aug. 28, 193'? M y 939i J. F.JAWOROWSKI 2,158,327

POWER TRANSMISSION AND SPEED REDUCER Filed Aug. 28, 1937 9 Sheets-Shee t3 J F. JawaRawsK/ y J. F. JAWOROWSKI 2,158,327

POWER TRANSMISSION AND SPEED REDUCER Filed Aug. 28, 1937 N 9Sheets-Sheet 4 3 wu onion .May 16, 1939. J. F. JAWOROWSKI POWERTRANSMISSION AND SPEED RFIDUCER Filed Aug. 28, 1937 9 Sheets-Sheet 5 m mw n W n, I a

May 16, 1939. J. F. JAWOROWSKI POWER TRANSMISSION AND SPEED REDUCERFiled Aug. 28, 1957 9 Sheetssheet 6 .rr .mwoowsm May 16, 1939. J. F.JAWOROWSKI 72,158,327

POWER TRANSMISSION AND SPEED REDUQER Filed Aug. 28, 1937 9 Sheets-Sheet7 m INN J r. .rnwanawsm 119 i 1 May 16, 93 J. F. JAWOROWSKI I 2,158,327

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Filed Aug. 28, 1937 9 Sheets-Sheet 9 #95.. 2 5k gush avg.. 02 .5 +2

2L 3 9.1 035k .5 09m t mak Patented May 16, 1939 UN IT E D ES E NT FF!(1 E POWER TRANSMISSION AND SPEED REDUCER Joseph FrJaworowski,Cleveland, Ohio Application August. 28, 1937, Serial No. 161,462

7 Claims.

This invention relates to powerv transmissions adapted to couple rotaryshafts with eachother and control their relative speeds or. direction'oimovement with respect to each other.

The invention has for its general object the provision of asemi-hydraulic power transmission for coupling rotary shafts-with eachother, which transmission permits of infinite variation of speed. inforward or reverse rotation between said shafts.

Further objects of the invention areto provide in a manner ashereinafter set forth, asemi: hydraulic power transmission of the classreferred to, which is comparatively simple in its construction andarrangement, strong; durable, compact, and highly eificient: in its use,whichtransmission embodies a simpleand-posi-tive cone trol; is readilyassembled'andin'stalled-withrespectto a driving member and-comparativelyinexpensive to manufacture.

With the foregoing and other objects in viewtheinvention consistsof thenovel construction. combination and arrangement of parts as hereinaftermore specifically. described, and'illustratedin the accompanyingdrawings; wherein is shown an embodiment of the invention, but'it istobe understood that changes; variations and-modificationscariberesortedto. which fall within the scopeoi the claims hereinto appended;

In the drawings wherein like reference char acters denote correspondingparts-throughout the several views:

line 3-3. of Fig. 1.

'Fig. 4 is across 4'-4 of Fig; 1.

Fig. 5 is a cross 5'5 of Fig. 1.

Fig. 6' is a cross 6E-of Fig. 1.

Fig. 7 isa cross- 1-7" oiFig. 1.

Fig. 8 is across S E of Fig. l. Fig; 9 he cross Sir-dorms. 1.

sectional sectional sectional 1 sectional sectional sectional view takenon: line View taken on line view. taken on line view taken on line viewtaken on line view taken on line Fig: lilis'a cross sectional view takenon line Fig, 11 isan end view of the semi-hydraulic power transmissionshowing the operating lever arrangement. a

Fig. 12 is an enlarged sectional view online l2-I2 of Fig. 11.

Figs. 13-25 are side views partly in section of the" disassembledsemi-hydraulic transmission.

Thus:

Fig. 13-is a sectional View: through the cover member carrying andsupporting the driven shaft with the ring gear andthe outsidebraketherefor, theshaft: and its bearing-s being shown in sideelevation.

Fig. 14 is a side elevation: of the assembled driving sectionrandcontroller section ofthe power transmission.

15is' a sectional view through the housing;

Fig. 16isa sectional view through the cover member, which member carriesandsupportsthe driveshaftof thedrivingsection and the controllersection.In this view the inner brake shoes which are attached to the cover andthe brake operating rod are shown in elevation.

Fig. l7is'a sectional-view through the guide andsupporting memberfor theoperating lever of the device.

Fig. 18 is a sectional view through the valve operating collar.

Fig. '19 through 24' are sectional views: through the couplingmember'which shiftablyconnectsthecollar with the rotatable operating,camlever of the device, thus:

Fig. 19 is a sectional view through awasher.

Fig. 20' is a sectional view, partly in-elevation, through the studdedring coupling the collar with the guide andsupporting member and withthe rotatable operating cam lever.

Fig. 21' is a sectional view through a second washer;

Figs. 22 and24 are sectional views of the nuts securing the studded ringcoupling to the collar.

Fig. 23 is a sectional View through the lockwasher interlocking. thenuts shown in Figs. 22 and-24, and

Fig. 25 is a side view partly broken away of the operating cam lever forthe power transmission.

The semi-hydraulic power transmission in accordance with the invention,comprises a driven sectionwhich is always connected-to the driven shaft,a driving section which is coupled with a motor, steam turbine, or otherprime mover, and an intermediate or controller section. However, as thethree above named sections partly encroach each other, no effort hasbeen made to individually describe each of the sections.

Referring to the drawings in detail, the reference character 2 indicatesa housing which forms a chamber 3. One end of this housing is closed bya cover plate 4 and its other end by a cover plate 5. The plates 4 and 5are screwed to the opposite ends of the housing 2 in any suitablemanner, as by bolts 6, which pass through bosses 1 provided for thispurpose in the plates 4 and 5, and each include, centrally thereof,laterally extending sleeves or hub portions 6 and 8 respectively, whichportions form bearing supports for the bearings of a driven shaft l4 anda drive shaft [5. The shafts l4 and i5 extend through the hub portions 8and 9 respectively and are provided with key ways l4, l5 to permit ofthe shafts being coupled with the device to be driven (not shown) and aprime mover (also not shown) Housing 2 at its top is bulged outwardly toform a longitudinal recess or channel l9, which channel is in opencommunication with the chamber 3. The wall of the channel i9 ispreferably provided with a threaded passage or opening H to permit ofoil or operating liquid being fed into the chamber 3, and this passageis closed by a removable, threaded taper plug l2.

To promote proper support of the driven shaft I4 in cover plate 4, thecylindrical inner wall of the extension or hub portion 8 seats the outerrings l8 of a pair of spaced ball bearings l9, IS, the inner rings 29 ofwhich are pressed upon the driven shaft l4. These ball bearings arespaced from each other by means of two telescoped sleeve members 2|, 22,the inner member 2! of which spaces the inner rings 29 and the outermember 22 of which spaces the outer rings 18. Preferably, as shown,member 22 is held in proper working position by means of a set screw 23,which screw engages a circumferential slot 23' in the outer wall of thesleeve member 22. A nut 24, secured to the threaded portion 25 of thedriven shaft l4 and held against rotation by means of a lock washer 26,prevents lateral movement of the ball bearings, the bearing ill of whichrests and seats against a circumferential shoulder 21 on shaft l4. Hubportion 8 is provided with a centrally perforated end wall 8', theopening 28 of which permits shaft l4 to be extended outwardly, and thecircumferential inner edge of said end wall is recessed as at 36 andseats a packing 29 within the recess to fluid tightly seal the shaft tothe hub portion and prevent escape of operating liquid. 1

The hub portion 9 on cover plate 5 mounts a sleeve bearing 3| for driveshaft l5. This bearing is pressed into a longitudinal bore 32 of saidhub portion, which bore is axially aligned with respect to shaft l4. Theshaft l5, which extends through cover plate 5 into chamber 3, supportsat its inner portion a controlling unit or member C which is coupledwith and rotatably mounted upon said shaft and has its inner endrotatably supported upon the inwardly extended reduced end 33 of thedriven shaft M, a roller bearing 34, engaging shaft I 4 and the axiallybored end 44 of the controlling member C being used for this purpose.The member C embodies a gear pump unit D with diametrically arrangedpumping sections E and F, which sections are symmetrically arranged withrespect to drive shaft l5 and directly coupled with said shaft forsimultaneous operation. The gear pump unit D embodies a disk-shaped body35 with flat end faces 36, 36' having secured thereto covers or closureplates 31, 38 respectively, which plates are removably secured to body35 by means of bolts 39. Closure plates 31, 38 are provided with hubs49, 4| respectively which carry sleeve bearings 42, 43, sleeved upon thedrive shaft IE to rotatably sup port unit D on said shaft, and shaft l5extends through closure plate 38, body 35 and with its bored end 44 intosleeve bearing 42 of hub portion 49. However, it should be noted thatshaft I5 is not fully extended through hub portion 40 to permit ofcommunication of the bored end 44 of said shaft with chamber 3 through aplurality of radial bores 45 in the bored central extension 46 of thehub 40, and therewith idle rotation of the gear pump unit D, as will belater described.

The body 35 of the pump unit D is formed with an irregularly shapedopening 4?, extending therethrough, which opening includes twodiametrically opposed, substantially circular portions 48 and 49, and acentrally arranged, substantially circular portion 59, which latterportion intersects with the portions 48 and 49-. The drive shaft l5extends centrally through the portion 50 and separates the portions 48and 49 from each other, which portions form individual working chambersfor the pumping sections E and F of the pump unit D. The part of thedrive shaft i5 which extends through the circular portion 50 of theopening 41 is enlarged in cross section and, at its periphery, providedwith gear teeth 5| adapted to mesh and engage with the teeth 52 of twogear wheels 53, 54, mounted for rotation in the respective circularportions or working chambers 48, 49 of the opening 41. Gear wheels 53and 54 include integral shafts 55, 56 respectively, which shafts aremounted in the closure plates 31, 38 and the hub portions 49, 4| ofthese plates, split bearings 51 and sleeve bearings 58 being used forthis purpose.

The cross sections of the circular portions 48, 49 of opening 4!correspond to the diameters of the gear wheels 53, 54, so that theirgear teeth 52 engage with the inner wall of the working chambers 48, 49.Preferably, as shown in Fig. 5, the walls of the working chambers arepartly undercut as at 59 to reduce pressure on gear wheels 53, 54 andshafts 55, 56.

In operation, liquid is drawn by suction of the pumping sections E and Ffrom chamber 3 into working chambers 48, 49 through intake passages 66,which passages communicatevwith intakes 6| of the working chambers 48,49 and with the lower portion of chamber 3. A single passage 62 in thehead plate 5 and housing 2 terminating slightly above the bottom wall ofthe chamber 3 feeds the liquid to both intake passages 60. This liquidis carried by the teeth of the gear wheels 53, 54 from the intakes 6! tothe outlets 63 of the Working chambers, thereafter discharged into andthrough a valve controlled passage 64 and passages 64 and finally fedback into the chamber 3 through the radial bores 45 in the bored centralextension 46 of the hub portion 40.

A piston like valve member 65 which is slidably arranged in the boredend of drive shaft l5 permits of the slots 64 in shaft l5 beingcontrolled and thus effects complete control of the liquid circulatedthrough pump sections E and F. Valve member 65 is connected to andcarried by a rod 66, slidably arranged in a reduced central bore 6'! inshaft l5. which bore is intersected by an elongated opening or slot 68in shaft l5. The slot 68 carries and guides a cross pin 69, coupled withthe end of the rod 66 and with a grooved collar 10, which collar isslidably mounted on shaft l5, and, when shifted, as hereinafterdescribed, effects shifting of rod 66 and valve member 65-, so as topermit of proper control and'.set'-- tingof the valve toany desiredposition.

Shafts 55 on-gear Wheels 53; 54 which, aspreviously" described; extendthroughfclosure plate 37, have their outer ends II formed with teeth T25meshing the teeth 13 oi" a flanged internal gear T4, thefiange I5 ofwhichis rigidly secured tothe enlarged portion '-16' of the driven shaftM by means of rivets Hi". The peripheral outer face H of internalgear-1'4-servesas 1 abrake drum for airexterna'librake; having brakeshoes' l8', l8 pivotally supported on pins T9; T9 andyieldingly held outof contact with theface II of: gear :T-L by means of springs 80; 80-;These-brake'shoes are provided with levee armsB-lv connected by meansof" a-link' 8'2 tea-lever 8I, which lever is sleeved: upon a shortshaft-84, in turn pivotally extended"through-saidhead-plate Apin 8|secureslever 8'I to-shaft 84-2 The operation of-lever 8 I- and therewiththe operation of the brake is effected by a rod 35, longitudinallyarranged Within longitudinal recess or channel I and pivotally mountedin cover plate The rod 85 extends with its squared end 86' into thesquare opening 81' in lever B'I andis thus-coupled with said lever,however,- any other suitable coupling may beused if so'desired.

-When shaft I5 is rotated ina clockwise direction and-valved passage Mis in fully opened position,- then pump sections-E and I are not underload, and consequently the toothed portions-II of'shafts 55, engaginginternal gear I4, rotate unit C in a clockwise rotation. Under thesecon'clitions shaft I4 is stationary because liquid or oil circulatingthrough pump sections E and F- flows therethrough andis freelydischarged from these sections.

When shaft I5 is rotated in a clockwise direction and valved passage 64is fully closed by valve member 65, thenthe gearwheels 53, 54-cannotrotate as the outlet openings of the p'umpsections are closed.Consequently the shaft I4 rotates in a clockwise direction with thespeed or the driving shaft I51 Whenshaft i5 is rotated ina clockwisedirectiona-ndvalved passage fifl is-partly-clos'ed by the valve member85', then unit C rotates in clockwise-rotation at a difierentialspeedwith respect to the drive shaft I5 and driven shaft I4 rotatesinclockwise rotation with a speedproportionate to thedifference in thespeeds-of -drive shaft I5and unit C.

It will now be seen that. the rotary movement of the driven shaftmay-be'varied' over:substantial ranges by manual orautomatic control ofthe valve member 6-5;.

A reverse rotary movementof: the drivenshaft canbe efiectedby arresting;rotation. of unit C.

This iseffected by'meansof aninternahbrake; l embodying-a brake. drum-8B,: rigidly secured-to the closure plate 33: by" means of bolts: 89,-and brake shoes 9G, El!! covered with abrakediningrdt. The brake shoes.99,. 9t are.pivotallyisecuredto the cover plate. 5 by headed belts 92andsyieldingly held out of centactwith-the, braking. face 93lofbrakeclrum. BS'by means of springs 94'; The opposed free ends of. brakeshoes ll', 9.6 are: cut on converging lines 95 for coeoperation with awedge-shaped member 96, which member forms the front portion of ashiftable plunger 91', longitudinall'y shiftably mounted in a chamberedbracket member 98, in turn' secured to a raised chambered portion I I!!!on cover plate' 5bymeans of bolts 99-. Portion IGIl'on cover late Sischambered topermit of said plunger beingextended into chamber3, so as toactuatethe internal brake, as will. be presently described; Thus,. chamberedbracket. member 98 pivotally mounts in its chamber IIII a doublelever. Hi2, pivotally supportedv upon apivot pin I03; This lever I62 hasoppositelyextended arms I84, 35, provided with rounded end. portions.The lever arm I04. extends through a slot I06 inplunger 9'! andslidablyengages theend III? of. a hardened pin I68, threadedly extended througha threaded-bore I89. in the outer. end of plunger 9? 'andJheld in ad.-justed. positionby a lock nut III and the lever arm I05 extends into aslot Ill of a bifurcated secondary plunger. H2, which latter is axiallyshiftably mounted in a bore I I3 of bracket member 98. An enlarged headportion M4 on the slotted inner end of plunger H2 limits itsaoutermovement and a roller IE5, pivotally secured. by means of: a pin II6between bifurcations IIE of said plunger, permits of rolling engagementof plunger II 2. with an. operating mechanism, hereinafter to bedescribed, for axially shifting plunger 9'! so as toactuate th internalbrake. A spring II'I, seated against a shoulder N8 of plunger. 9.? andthe inner wall IIEl of bracket member 98', shifts plunger 9? inwardlywhen plunger H2 is released from rollingc-ontact with the. operatingmechanism referred to above. 'I'hisoperating mechanism embodies acylindrically shaped cam member I rota-tably secured to" cover plate 5by means of a substantially cylindrically shaped, flanged cover memberI2'I', which cover member is connected to said cover plate 5 by means ofbolts I 22, extended through-openings 1232 in the flange I24 of saidcover member, and-which member has its outer end closed byaperturediplate I25, secured to said member by bolts I26. Thecylindrical sidewall IZ'I of member I2] is out awayat I28to permit of alever I29 being extendeditherethrough and shifted through an arc ofapproximately 90. Cam member I 20 supports lever I29 and is coupled withthe collar- Ili'onthe-drWe shaft Ifs by means of a ring memberI30p1'ovided with diametrically opposed short studs I3I. These studsextend through inclined slots I32in cam member I20 and are guided" instraight recesses I33 in cover member IZI to prevent rotation of ringmember I39, whenshaft I5 and'collar II! are jointly rotatedl A pair ofthrust washers I34, I34, engaging the opposite sides of the ringmemberIiiil'take up-lat'eralstresses duringshifting operations, which washersseat against a fiange I35 on collar H3 and are held in proper positionby nuts 63%, I 3! and a lock Washer I38, engaged with the threaded andkeyed'end I39 of collar"). v I

Lever' I29 carries and actuates the outer and inner brake members bymeans of a cam member I'4 I adjustably connected to lever I29 by boltsI42. These bolts are extended through; a slot I 43i'n-leverI29andthreadedlyengage with cam member MI; The cam member MI embodies abeveled face I44 adapted to engage the roller I I5 at the end of'plungerH2 and effect inward movement of the plunger 91 and therewith operationof the internal brake, and the upper end of cam member MI is reduced inwidth and the edge formed with a circular recess I45 to permit of a"lever I46, coupled with rod 85',- being lifted thereby and held when aroller Id! at the end of lever I46 is riding upwardly on the inclinededges M't of'the cam MI, when member lzdand'op erating lever I29 areshifted from. the dash. double-dotted line position of- Fig. 10 tothe'full line positionofthis-figure, It will now-be seen that lever I46,which lever is coupled with the outer end I48 of the rod 85, effectsactuation of the valve member 64, the outer brake member and the innerbrake member.

In operation of the power transmission, drive shaft I5, which is drivenby a prime mover, effects circulation of a body of liquid, which liquidis stored in chamber 3 and preferably of high conductivity, high boilingpoint, good lubricating qualities and high viscosity. When the operatinglever is in neutral position cam member MI and the operating lever I29are in the full line position of Fig. 10. In this position the gear pumpunit draws liquid from chamber 3 through passages 62 and 60 into theintakes SI of the two working chambers 48, t9, feeds such liquid throughthe pump sections and their outlets 63 into and through the fully openedvalved passage 64 and finally discharges the liquid into and through thebored end of the unit C through radial outlet bores back into thechamber 3.

In such neutral position of the transmission operating cam member I20has shifted ring member I30 and valve member toward the right, andconsequently the valved passage 64 is unobstructed and permits of theliquid being freely discharged from pmnp sections D and E back intochamber 3. The circular notch I45 at the top of the cam member I 4!holds lever I46 in raised position and therewith rod 85, so that link 82draws brake shoes '18, I8 against the brake surface I! of the ring gearI4, thus insuring arrest of ring gear I4 and driven shaft I4 coupledtherewith.

To efiect rotation of the driven shaft in the direction of rotation ofthe drive shaft, operating lever I29 is shifted toward the left to dashdouble dotted position (Fig. 11). In this case lever I29 and valvemember 65 are in Fig. 1

a position, in which outlet passage 55 for pump unit D is fully closedand gear wheels 53, 54 are prevented from rotation, so that unit Cdirectly couples the drive shaft and the driven shaft with each other.When operating lever I29 is located between the neutral and the lastdescribed position, then valved passage 64 is partly restricted,therefore the gear wheels 53 and 54 rotate with a speed lower than theirrotary movement in the neutral position of lever Should it be desired torotate the driven shaft in a direction opposite to the rotation of thedrive shaft, then operating lever I 29 is shifted toward the right toeffect engagement of the beveled face I44 of the cam member I4I with theroller H5 and therewith shifting of plunger II2 inwardly for actuationof the internal brake, so as to stop rotation of unit C, which of courseeffects a reversed rotation of the driven shaft I4 by the drive shaftI5.

The internal brake of the mechanism described effects coupling of thecontroller section with the driven and drive shaft or with the housing,and also permits of a free rotary action of the mechanism.

The described power transmission according to the invention permits ofinfinite variations of the speed of the driven shaft in oppositedirections with a driving shaft rotating at constant speed in onedirection. Unit C, when rotating at high speed acts as a fly wheel andthus effects uniform and steady run of the prime mover coupled with thedrive shaft.

Although I have illustrated and described a preferred embodiment of myinvention, yet it is to be understood, that changes in the details ofconstruction can be had which will fall within the scope of theinvention as claimed.

Having thus described my invention, what I claim is:-

1. A power transmitting and speed reducing unit comprising a casing, adrive shaft and a driven shaft, said shafts extending from oppositesides into said casing, a member for coupling said shafts rotatablymounted within said casing upon said shafts, valve controlled pumpingmeans within said coupling member embodying rotors directly coupled withsaid drive shaft, and pinions at the ends of said rotors, a ring gearconnected to the driven shaft in driving connection with said pinions,valve means controlling the rotors of said pumping means, a brake forsaid ring gear, a brake for said coupling member, and means including asingle operating lever for jointly actuating said valve means and oneand/or the other of said brakes.

2. A power transmitting and speed reducing unit comprising a casing, adrive shaft and a driven shaft, said shafts extending from oppositesides into said casing, a member for coupling said shafts rotatablymounted within said casing upon said shafts, valve controlled pumpingmeans within said coupling member embodying rotors directly coupled withsaid drive shaft and indirectly coupled with said driven shaft by meansof a ring gear and pinions, valve means controlling the rotation of therotors of said pumping means, braking means for said coupling member,braking means for said driven shaft, and means including a singleoperating lever for actuating said valve means and said braking means.

3. A power transmitting and speed reducing unit as described in claim 1,wherein said braking means for said driven shaft and said braking meansfor said coupling member are individually actuated by the lever of saidactuating means.

4. A power transmitting and speed reducing unit as described in claim 1,wherein said drive shaft embodies an axial bore, wherein said pumpingmeans include outlet passages terminating in the bore of said driveshaft, wherein said valve means are slidably arranged in the bore ofsaid drive shaft for controlling the open ends of said outlet passages,and wherein said actuating means has its lever coupled with said valvemeans.

5. A power transmitting and speed reducing unit comprising a casing, anaxially bored drive shaft, a driven shaft, said shafts being axiallyaligned and extending from opposite sides into said casing in spacedrelation with respect to each other, a member for coupling said shaftswith each other having an axial bore for rotatably mounting said memberon said shafts, passage means in said member for open communication ofits bore with said casing, said passage means being arranged inalignment with the space between said shafts, valve controlled pumpingmeans within said coupling member embodying rotors directly coupled withthe drive shaft and indirectly coupled with the driven shaft by means ofa ring gear and pinions, said pumping means including inlet means incommunication with said casing and outlet means in communication withthe bore of said drive shaft, and shiftable valve means within the boreof said drive shaft for controlling the said outlet means, saidshiftable valve means embodying mechanism for actuation of said valvemeans from the outside of said casing.

6. A power transmitting and speed reducing unit as described in claim 5,embodying a brake for said driven shaft, a brake for said couplingmember, and actuating means embodying means coupling said actuatingmeans with said valve means and said brakes for joint actuation of saidvalve means and said brakes.

7. A power transmitting and speed reducing unit as described in claim 5,embodying an external brake for said driven shaft, an internal brake forsaid coupling member and a lever for actuating said valve means and saidbrakes, said lever embodying means for coupling same with said valvemeans, and cam means for actuating said brakes to efiect operation ofsaid valve means and brakes by a rocking movement of said lever.

JOSEPH F. JAWOROWSKL

